Spinning apparatus



P 1964 E. oRTMANs 3,150,480

SPINNING APPARATUS Filed March 1, 1963 3 Sheets-Sheet 1 FIG.1

SPINDLE SPEED 1 L POSITIONS INYENT'OR:

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SPINNING APPARATUS Filed March 1, 1963 3 Sheets-Sheet 2 INVENTOR- fmmgORTMHNS P 1964 E. ORTMANS 3,150,480

SPINNING APPARATUS Filed March 1, 1963 3 Sheets-Sheet 3 IvvE'NraR f'pqmiGem/9N United States Patent Oh ice 3,150,480 SPlNNlNG APPARATUS Emile@rtrnans, 52 Rue de Liege, Verviers, Belgium Filed Mar. 1, 1963, Ser.No. 262,5)09 Claims priority, application Belgium, Mar. 6,1 62,

In the textile industry frames are already known which spin and producecops on bobbins simultaneously which, in principle, include a feedingsystem supplying the material to be spun in the form of slivers, a conefor forming the cop which rotates at a constant speed to give the twistto make the yarn, a member which is concentrically disposed to the coneand turns with the same speed thereof and has at the same time areciprocating movement, a spindle carrying the bobbin, the spindlehaving a rotational speed differing as to that of the cone to cause thewinding of the yarn onto the spindle while the member moving up and downcauses the yarn to twist from bottom to top and from top to bottom onthe head of the bobbin located in the formation cone.

In the known frames for spinning and producing cops, the rotationalspeed of the spindle carrying the bobbin is constant. Also the formationcone, the member moving up and down and the spindle carrying the bobbinare driven by means which do not allow any slipping like that as causedby gears or possibly by a chain.

The known frames for spinning and producing cops have severaldisadvantages.

The increase in the twist in the yarn is obtained by increasing thespeed of the spindle and the decrease of the twist is obtained byslowing the speed of the spindle, that is, in decreasing or increasingrespectively the speed of winding the yarn, which for a given speed ofthe formation cones causes a decrease or an increase of the speed of thefeed system. Furthermore when the frame is set in motion, the speed ofthe feed system is jerking to such an extent that before it is runningsmoothly, it often causes yarn breakages by over or under tension whichresults in loss of time and material. It can also occur that the speedchosen for the spindle produces a synchronism in the winding of the yarnon the bobbin which will cause an exact juxtaposition of the layers ofyarn, one on the other, and thereby produce a cop having no rigidity andwhich will eventually crumble and be difficult to handle. Actually onetries to suppress this fault as soon as it is noticed by slightlymodifying, by degrees, the speed of feed.

During the formation of the cop on the bobbin, the differences in thespeed of the winding of the yarn produced by the winding from a small toa large diameter and vice versa are corrected by causing the speed ofthe entry of the yarn into the formation cones to vary correspond ingly,which is actually brought about by a correcting balance lever over whichthe yarn passes and which is located between the feed system and thecone. However, this balance lever limits the speed of the feed and, inview of the difiiculty encountered in moving it rapidly, it continuouslymodifies the length of the yarn being twisted and thereby prevents therational utilization of the draw rollers.

The present invention, which proposes to eliminate the disadvantages ofknown frames for spinning and producing cops on bobbins, consists inmaking interdependent,

the controls of each of the groups of parts whose respective movements,indispensable for making the yarn and winding it into cops, are thusconstantly co-ordinated in such a way that a modification of one ofthese movements reacts on the others which are thus automaticallymodified in a corresponding manner.

3,159,480 Patented Sept. 29., 1964 In other words, according to thepresent method the control of the parts forming one group is caused-toact on the control of the parts forming another group in order tomaintain a continuous reciprocal co-ordination of their respectivemovements.

Accordingly, an essential characteristic of the application of the abovemethod to a frame for spinning and pro ducing cops on bobbins is thatthe main control shaft drives at given speeds the driving shaft for thecones and the primary shaft of a first differential and at differentspeeds, obtained by changes in the gearing, the planet wheel carrier ofthe said first differential and the primary shaft of a seconddifierential which has a planet wheel carrier mounted on the outputshaft which drives the spindles and which in turn is controlled by a cammounted on the output shaft of the first differential whichsimultaneously reciprocates the member of the feed system.

ther characteristics will become apparent in the following descriptionof the attached drawings which show, by way of example only, anembodiment of the invention.

In these drawings:

FIG. 1 is a schematic front view, partly in elevation, and partly insection, showing the first differential to control the feed of theformation cones and the reciprocating members and the seconddifferential to control the spindles.

FIG. 2 is a diagram showing the variation of the speed of the spindlesaccording to the position of the reciprocating members.

FIG. 3 is a schematic view in elevation of the head of a bobbin in aformation cone shown in section.

FIG. 4 is a schematic View partially in side elevation to show thecontrol of the formation cone and of the reciprocating member.

FIG. 5 is a schematic view partially in side elevation to show thecontrol of the spindles.

FIG. 6 is a partial schematic view of the movement control of thetraversing member.

FIG. 7 is a partial view in plan of the arm bearing the fingersactivating the traversing members.

FIG. 8 is a partial schematic view of the conventional cop-formingmechanism.

The figures show only the parts necessary to understand the inventionand for clarity certain parts have been omitted as in the FIGS. 4 and 5.

Referring now to the figures, it will be seen that the strands 2b of theweb of textile fibres pass from the feed roller 2 to the deliveryrollers 3 from where they are guided towards the rotating formationcones 4 ending in the sleeves 4-0 on whose upper end the gears 5 aremounted. These gears engage the pinion 6 which is carried by the controlshaft t t: which is driven by the shaft '7 from the bevel gears 7a. Theshaft 7 which forms the main control shaft of the frame is driven by thegrooved pulley 8a which in turn is driven by the transmission belt 8passing over the grooved pulley 9a: mounted on the shaft 9 driven by themotor ll.

This shaft 7 carries on its other end the pinion 1%) driving the pinion11, which drives the pinion 12 mounted on the primary shaft 13 of thefirst differential. This first difierential consists of a primary pinion14 which drives the part 15a of a planetary wheel having a part 1511driving a secondary output pinion 16 mounted on an output shaft 17. Apinion 18 is located on this shaft 17 and meshes with the pinion 19which drives the pinion 29 mounted on the shaft 21. The shaft 21 carriesthe pinion 21a which drives the pinion 2a of the feed roller 2, and thepinion 3a of the delivery rollers 3 by a flexible transmission means21b. Two cams 22 and 23 are also mounted on the shaft 21. The first ofthe cams 22 serves as a track for the follower 24 carried by the lever25 pivoted at a in relation to the frame. To lever 25 is articulated aconnecting rod 26 which is articulated in the opening 271: of thepivoting toothed sector 27. When cam 22 pushes the lever in thedirection of arrow X, sector 27, pivoting around 27a clockwise,entrains, by means of its teeth 27c, sector 28 which pivots around 28ain a counterclockwise direction. This pivoting urges the teeth 231),which engage with rack 29, to slide arm 29a upward. This arm 2% supportsa series of fingers, each of which fits in a groove in the reciprocatingmembers 31. These members 31 are thus moved upwardly as they slide overthe sleeves 4a. As a result of this movement, the thread which was woundon the large diameter d of the end of the cocoon is gradually induced towind on an ever smaller diameter until it reaches the diameter d1. Assoon as these members have reached the end of their upward stroke, cam22 returns lever 25 in the direction opposite to X and all the otherparts act in the opposite way as heretofore mentioned, so that themembers 31 are returned downwardly and the thread gradually returns towind on the large diameter of the end of the cop. As a result of thesenecessary movements of the members 31, the spindles have to rotate atvariable speeds. This is achieved by a second differential. With this inmind, the drive shaft 7 supports the pinion 10 which engages with thepinion 11 mounted on the shaft 32 mounting the pinion 33 which in turndrives the pinion 34 which engages with the pinion 37 mounted on theshaft 33 bearing the primary pinion 39 which engages with the pinion 40awhich drives 4% engaging the pinion 41, which drives shaft 42 which, bypinions 49 and 5t), drives the spindles 48.

A pinion 4C: is fixed on the primary shaft 33 of the second differentialand drives the pinions 44, 45 and the pinion 46 fixed on the bushing 47aof the planet wheel carrier 47 of the first differential (FIG. 1). Theparts 40a, 40b forming the planet wheel gear of the second differentialare mounted on the planet wheel carrier 51 which has a sleeve 52 coaxialto the shaft 4-2 around which it can oscillate due to the ball bearings53. This sleeve 52 has an arm 54 (FIG. 5) at the end of which isarticulated an arm 55 which is articulated at its upper end in a slot 56provided in the lever 57 pivoted at 58 on the frame and carrying thefollower 59 rolling on the cam 23 fixed to the shaft 21 which is drivenby the output shaft of the first differential and thus driving asexplained above the feed system for the reciprocating member.

A continuous co-ordination is established by the assembly which has justbeen described between the control shaft 6a of the formation cones 4,the control shaft 21 of the members 31 and the feed system 2 and thecontrol shaft 42 of the spindles 48. If it is desired to increase thetwist of the yarn, the driving pinions 33 and 37 on the shaft 33 can beexchanged so as to cause shaft 38 to turn more quickly and consequentlycause the pinions 44, 45 and 46 and the planet wheel carrier 47 to turnmore quickly. In this differential if the planet wheel carrier advancesin the sense of the pinion of entry, a slowing down or even a stoppageof the output pinion is produced, and therefore, as the planet wheelcarrier 47 turns faster, the output shaft 17 turns more slowly and theshaft 21 also turns more slowly so that the reciprocating member 31 andthe feed system 2 are driven at a reduced speed.

When the yarn winds from the large diameter d of the cop to the smalldiameter d1 (FIG. 3), the members 31 should move upwardly and the cam 22should be regulated to urge the lever 25 downwardly (FIG. 4), becausethe winding has to be maintained constant and therefore the rotationalspeed of the spindles 48 must decrease.

This is brought about automatically by the second differential whoseplanet wheel carrier 51 turns slightly in the sense of the pinion 39 andof the shaft 3, which results from the action of cam 23 on the follower59 of the pivoted arm 57 driving the arm 55 joined to the arm 54 of thesleeve 52 provided with the planet wheel carrier 51. The operations takeplace in reverse when the yarn passes from the diameter d1 to thediameter d.

In the event that a cop with an outside diameter D (FIG. 3) is to beobtained, the members 31 must execute a greater displacement,corresponding to L which is the height of the end of the cocoon to beobtained, as compared to the displacement I when a diameter d is to beobtained, and the strand will have to be wound from diameter D todiameter di and vice versa. To extend the stroke of these members, thearticulation of connecting rod 26 to the sector 27 is moved closer tothe pivot point 27a. Inasmuch as the difference in the diameters of theend of the cocoon is increased, it will also be understood that thevariations in speed of spindles 48 must be greater, so that thevariations in speed of shaft 42 must be greater, which is accomplishedby moving the arm 55 in the slot. 56 of lever 57 away from the pivotpoint 53.

The variations of the speeds of the spindles according to thereciprocating members are shown in FIG. 2 in which the speeds are inordinate and the positions in abscissa. The curve A corresponds to thebobbin having an exterior diameter d and the curve B to that having adiameter D.

Apart from the foregoing, however, the formation of the cop on thebobbin is quite conventional. The strands 2b of the sheet of textilefibers, which come from the feed roller 2, pass to the delivery rollers3 whence they pass into the inside of sleeves 4:: that terminate in thecones d. A slot. 4-1) is provided through cone 4 along a generatrix ofthe cone. Cone 4, by its rotation, twists the strand 2b and transformsit into a thread which passes through opening 31b and thence over rim31a. The strand is secured at one end to bobbin head 48a which in turnslides axially on spindle 48 and rotates with spindle 48. The thread isthereafter twisted and wound on the cop holder in successive superposedlayers in such a way as to form a cop whose end is conical, the windingbeing done back and forth between the large and the small diameter ofthe cop by the reciprocatory movement of member 31. The rotating cones 4thus remain at a fixed level and do not reciprocate axially; and pinions5 are thus carried by sleeves 4a and engage with pinion 6 mounted onshaft 7a rotating under the influence of pulley 8a which in turn ismounted on shaft 7, and so on back through the drive train includingbelt 8, shaft 9 and motor 1.

Therefore, cone 4 serves to twist the strand and transform it intothread, while spindle 48, rotating at a different speed from cone 4,winds the thread into a cop. Upon such winding, the cop grows in axialextent because it is formed of superposed layers of wound thread. Theselayers build up between the cop holder and the inner face of the cone,and automatically effect the axial displacement of the cop and the copholder along the spindle, moving the cop holder away from the hollowcone as the cop extends. In FIGS. 1, 4, 5 and 8, this would be observedas a progressively downward movement of member 4301. In effect,therefore, the conical upper end of the cop remains at the same axiallocation relative to cone 4, the growth of the cop being accommodated bymovement of the building cop away from the formation cone.

What I claim is:

1. Apparatus for spinning and winding filamentary material into cops,comprising means for feeding strands to the apparatus, a cone forforming a cop, drive means for rotating the cone at a constant speed totwist the strands, a member concentric with the cone, means mountingsaid member for rotation with and for axial reciprocatory movementrelative to the cone, 2. spindle for carrying the cop, means forrotating the spindle at a speed different from that of the cone to causethe thread to be wound into a cop, first differential means for drivingthe feed means at varying speeds and for reciprocating said member,second differential means for driving the spindle at varying speeds, anddrive means common to said first and second differential rheans and tosaid cone drive means.

2. Apparatus as claimed in claim 1, said first and second differentialmeans being so interconnected as to drive said feeding means and saidspindle at speeds Whose ratio to each other varies.

3. Apparatus as claimed in claim 1, said first and second differentialmeans comprising planetary gearing.

4. Apparatus as claimed in claim 1, said last-named drive meanscomprising a main drive shaft, a shaft driven by said main drive shaftand driving said cone and said first and second differential means, saidsecond differential means having planetary gearing including a planetwheel carrier and an output shaft on which said planet wheel carrier ismounted, said output shaft driving said spindle, said first differentialmeans having an output shaft, and a cam driven by the output shaft ofsaid first diiferential means and drivably interconnected with saidplanet wheel carrier to control the position of said planet Wheelcarrier.

5. Apparatus as claimed in claim 4, and a further cam driven by saidoutput shaft of said first ditferential means, a follower traveling onthe profile of said furtherTain an arm carrying said follower, a crankarm articulated to said arm, a first toothed sector articulated to saidcrank arm, a second toothed sector sWingably driven by said firstsector, a rack meshing with said second sector, an arm carried by saidrack, and a rod on said arm for reciprocating said member.

6. Apparatus as claimed in claim 4, and a follower traveling on theprofile of said cam, a lever carrying said follower, a rod pivotallyarticulated to said lever, and an arm connected to said rod, said armbeing in unitary assembly with the planet Wheel carrier of the seconddifierential means which thus is given an oscillatory movement.

7. Apparatus as claimed in claim 4, and a further cam driven by saidoutput shaft of said first differential means to reciprocate saidmember.

8. Apparatus as claimed in claim 7, said further cam being so disposedthat on movement of said member in one direction, the planet Wheelcarrier of the second differential means turns in the sense implied bythe ratio of the pinions on said second differential means toternporarily slow down the speed of rotation of the output shaft of saidfirst differential means and on movement in the opposite direction theplanet wheel carrier of the second differential turns in the oppositesense to temporarily increase the speed of rotation of the output shaftwhich controls the spindles.

9. Apparatus as claimed in claim 5, said first toothed sector having aslot, and means for selectively adjustably fixing said crank arm at anyof a plurality of desired positions along the length of said slotthereby to alter the magnitude of the movements of said member.

10. Apparatus as claimed in claim 6, said lever carrying the follower onthe second cam having a slot therein, and means for adjustably fixingsaid rod in any of a plurality of positions along said slot thereby toregulate the magnitude of the movement of said planet wheel carrier ofsaid second diiferential means.

11. Apparatus as claimed in claim 4, the planet wheel carrier of saidsecond differential means being mounted for oscillatory movement aboutsaid output shaft of said second diiferential means.

References Cited in the file of this patent UNITED STATES PATENTS1,178,447 Hoenig Apr. 4, 1916 1,862,030 Oertel June 7, 1932 2,585,823Norcross Feb. 12, 1952 2,785,527 Lewellen et a1 Mar. 19, 1957 2,946,244Drtina June 14, 1960 2,996,870 Pornes et a1 Aug. 22, 1961 FOREIGNPATENTS 836,997 Great Britain June 9, 1960

1. APPARATUS FOR SPINNING AND WINDING FILAMENTARY MATERIAL INTO COPS,COMPRISING MEANS FOR FEEDING STRANDS TO THE APPARATUS, A CONE FORFORMING A COP, DRIVE MEANS FOR ROTATING THE CONE AT A CONSTANT SPEED TOTWIST THE STRANDS, A MEMBER CONCENTRIC WITH THE CONE, MEANS MOUNTINGSAID MEMBER FOR ROTATION WITH AND FOR AXIAL RECIPROCATORY MOVEMENTRELATIVE TO THE CONE, A SPINDLE FOR CARRYING THE COP, MEANS FOR ROTATINGTHE SPINDLE AT A SPEED DIFFERENT FROM THAT OF THE CONE TO CAUSE THETHREAD TO BE WOUND INTO A COP, FIRST DIFFERENTIAL MEANS FOR DRIVING THEFEED MEANS AT VARYING SPEEDS AND FOR RECIPROCATING SAID MEMBER, SECONDDIFFERENTIAL MEANS FOR DRIVING THE SPINDLE AT VARYING SPEEDS, AND DRIVEMEANS COMMON TO SAID FIRST AND SECOND DIFFERENTIAL MEANS AND TO SAIDCONE DRIVE MEANS.